JP2015535205A - Transmission and operating method thereof - Google Patents

Transmission and operating method thereof Download PDF

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Publication number
JP2015535205A
JP2015535205A JP2015538377A JP2015538377A JP2015535205A JP 2015535205 A JP2015535205 A JP 2015535205A JP 2015538377 A JP2015538377 A JP 2015538377A JP 2015538377 A JP2015538377 A JP 2015538377A JP 2015535205 A JP2015535205 A JP 2015535205A
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planetary gear
gear set
transmission
drive
operated
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JP2015535205A5 (en
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リヒテネッガー，シュテファン
エアヤヴェッツ，コンスタンティン
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AVL List GmbH
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AVL List GmbH
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Priority claimed from ATA50464/2012A external-priority patent/AT512912B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • F16H3/725—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines with means to change ratio in the mechanical gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2025—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 5 connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors
    • Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
    • Y10S903/904—Component specially adapted for hev
    • Y10S903/915—Specific drive or transmission adapted for hev
    • Y10S903/917—Specific drive or transmission adapted for hev with transmission for changing gear ratio

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

本発明は、一次駆動軸（１６）を備える一次駆動装置を有するドライブトレインを備える、特に車両用の、トランスミッション（１）であって、二つの太陽歯車軸（１０，１３）、一つの遊星キャリア軸（１８）及び少なくとも一つの内歯車軸（１２）を有するダブル遊星歯車を有するラビニヨ型遊星歯車組（２）並びに、更に、減速歯車装置として形成され、かつ、歯車エレメントとして太陽歯車（５ａ）、遊星キャリア（８ａ）及び内歯車（６ａ）を備える、上流側シングル遊星歯車組（３）を備えるトランスミッション（１）に関する。シングル遊星歯車組（３）の歯車エレメントの第一の歯車エレメント、具体的には、太陽歯車（５ａ）は、ハウジングに固定されるように形成されている。本発明によれば、ラビニヨ型遊星歯車組（２）の少なくとも第一エレメントは、特に好ましくは電気機械によって形成された二次駆動装置（２１）に、好ましくは恒久的に、駆動接続されている。The invention relates to a transmission (1), in particular for vehicles, comprising a drive train with a primary drive comprising a primary drive shaft (16), two sun gear shafts (10, 13), one planet carrier. Ravigneaux type planetary gear set (2) having a double planetary gear having a shaft (18) and at least one internal gear shaft (12), and further a sun gear (5a) formed as a reduction gear device and as a gear element And a transmission (1) comprising an upstream single planetary gear set (3) comprising a planet carrier (8a) and an internal gear (6a). The first gear element of the gear element of the single planetary gear set (3), specifically, the sun gear (5a) is formed to be fixed to the housing. According to the invention, at least the first element of the Ravigneaux planetary gear set (2) is particularly preferably permanently connected to the secondary drive (21), preferably formed by an electric machine. .

Description

本発明は、一次駆動軸を備える一次駆動装置を有するドライブトレインを備える、特に車両用の、トランスミッションであって、二つの太陽歯車軸、一つの遊星キャリア軸及び少なくとも一つの内歯車軸を有するダブル遊星歯車を有するラビニヨ型遊星歯車組並びに減速歯車装置として形成され、かつ、歯車エレメントとして太陽歯車、遊星キャリア及び内歯車を備え、前記歯車エレメントの第一の歯車エレメントがハウジングに固定されるように形成された上流側シングル遊星歯車組を備えるトランスミッションに関する。更に、本発明は前記トランスミッションの作動方法に関する。   The invention relates to a transmission, in particular for a vehicle, comprising a drive train with a primary drive comprising a primary drive shaft, a double having two sun gear shafts, one planet carrier shaft and at least one internal gear shaft. It is formed as a Ravigneaux type planetary gear set having a planetary gear and a reduction gear device, and includes a sun gear, a planet carrier and an internal gear as gear elements, and the first gear element of the gear element is fixed to the housing The present invention relates to a transmission including a formed upstream single planetary gear set. Furthermore, the present invention relates to a method for operating the transmission.

上述したタイプのトランスミッションは、米国特許第５１０６３５２号明細書から知られている。そのような所謂ルペルシェ型トランスミッションは、車両の自動トランスミッションに使用され、それは所謂ラビニヨ型組、ダブル遊星歯車、の更に発展したものである。前記ルペルシェ型組は、ラビニヨ型組の手前に別のシングル遊星歯車組が設けられ、クラッチによって接続されている構成で製造される。前記シングル遊星歯車の内歯車はエンジン駆動軸に接続されている。このことは、前記シングル遊星歯車組がアイドリング運転中、常時同時回転される、ということを意味する。パワーテイクオフはラビニヨ型組の内歯車を介して行われ、これはディファレンシャルギヤを介して駆動車輪に接続されている。前記シングル遊星歯車組の太陽歯車は、恒久的に回転停止されている。多数のクラッチと制動だけでなく、例えば流体動圧トルクコンバータ等の別体の加速装置が必要とされることが欠点である。   A transmission of the type described above is known from US Pat. No. 5,106,352. Such so-called Ruperche type transmissions are used in automatic transmissions of vehicles, which is a further development of the so-called Ravigneaux type set, double planetary gears. The Rupelche type group is manufactured in a configuration in which another single planetary gear group is provided in front of the Ravigneaux type group and connected by a clutch. The internal gear of the single planetary gear is connected to the engine drive shaft. This means that the single planetary gear set is always rotated simultaneously during idling operation. The power take-off takes place via Ravigneaux type internal gears, which are connected to the drive wheels via differential gears. The sun gear of the single planetary gear set is permanently stopped. The disadvantage is that not only a large number of clutches and brakes but also a separate acceleration device such as a fluid dynamic pressure torque converter is required.

独国特許出願公開第１０２００４０５３０４４号明細書は、ダブル遊星歯車組とシングル遊星歯車組とを備えるハイブリッド駆動用のトランスミッションを開示し、そこでは、前記ダブル遊星歯車組の各太陽歯車軸は各電気機械に駆動接続されている。   DE 102004053044 discloses a transmission for a hybrid drive comprising a double planetary gear set and a single planetary gear set, wherein each sun gear shaft of said double planetary gear set is connected to each electric machine. Connected to the drive.

米国特許第５１０６３５２号明細書US Pat. No. 5,106,352 独国特許出願公開第１０２００４０５３０４４号明細書German Patent Application No. 102004053044

本発明の課題は、前述した欠点を回避するとともに、上述したタイプのトランスミッションにおいて、少ない作動力及び少ない必要空間で、高い機能性を達成することにある。   The object of the present invention is to avoid the above-mentioned drawbacks and to achieve high functionality in a transmission of the above-described type with a small operating force and a small required space.

これは、本発明によれば、前記ラビニヨ型遊星歯車組の少なくとも第一のエレメントが二次駆動装置に、好ましくは恒久的に、駆動接続されることによって達成される。前記二次駆動装置は、有利には電気機械によって形成することができる。これによって、前記一次駆動装置及び前記二次駆動装置を有利に組み合わせる、又はこれらを二者択一的に交互に使用することが可能となる。   This is achieved according to the invention in that at least the first element of the Ravigneaux planetary gear set is drivingly connected, preferably permanently, to a secondary drive. The secondary drive device can advantageously be formed by an electric machine. This makes it possible to advantageously combine the primary drive device and the secondary drive device, or alternatively to use them alternatively.

前記ラビニヨ型遊星歯車組の第二エレメントは、有利には制動装置によって回転停止することができる。   The second element of the Ravigneaux planetary gear set can advantageously be stopped by a braking device.

前記ラビニヨ型遊星歯車組の第三エレメント、好ましくは前記ラビニヨ型遊星歯車組の第一太陽歯車軸が、前記シングル遊星歯車組の第二歯車エレメント、好ましくは前記シングル遊星歯車組の前記遊星キャリアに駆動接続される、又は駆動接続可能であると特に有利である。   The third element of the Ravigneaux planetary gear set, preferably the first sun gear shaft of the Ravigneaux planetary gear set, is connected to the second gear element of the single planetary gear set, preferably the planet carrier of the single planetary gear set. It is particularly advantageous if it is drive-connected or drive-connectable.

前記ラビニヨ型遊星歯車組の前記第一エレメントは、第二太陽歯車軸によって形成することができ、前記第二エレメントは、前記遊星キャリア軸によって形成することができる。これに代えて、前記第一エレメントを前記ラビニヨ型遊星歯車組の前記遊星キャリア軸によって形成し、前記第二エレメントを前記ラビニヨ型遊星歯車組の前記第二太陽歯車軸によって形成することもできる。その結果、必要空間と機能的要請に関する特別の要望を達成するために、前記ラビニヨ型遊星歯車組の内部における前記二次駆動装置と前記制動装置の位置を有利に入れ替えることが可能となる。   The first element of the Ravigneaux planetary gear set can be formed by a second sun gear shaft, and the second element can be formed by the planet carrier shaft. Alternatively, the first element may be formed by the planet carrier shaft of the Ravigneaux planetary gear set, and the second element may be formed by the second sun gear shaft of the Ravigneaux planetary gear set. As a result, it is possible to advantageously exchange the positions of the secondary drive device and the braking device within the Ravigneaux planetary gear set in order to achieve special requirements regarding the required space and functional requirements.

前記第一太陽歯車軸及び前記第二太陽歯車軸は、異なる回転方向を有する。なぜなら、第一太陽歯車軸は、第一遊星歯車組を介して第二遊星歯車組に作用するのに対して、前記第二太陽歯車軸は、第二遊星歯車組に直接作用するからである。   The first sun gear shaft and the second sun gear shaft have different rotation directions. This is because the first sun gear shaft acts on the second planetary gear set via the first planetary gear set, whereas the second sun gear shaft acts directly on the second planetary gear set. .

本発明の別の変形構成によれば、前記ラビニヨ型遊星歯車組の前記第一エレメントは、第二内歯車によって形成されている。前記二次駆動装置は、速度段を介して、又は直接的に、前記第二内歯車に駆動接続することができる。この構成は、第二無段動力分配作動範囲が実現可能となる、という利点を提供する。   According to another modified configuration of the present invention, the first element of the Ravigneaux type planetary gear set is formed by a second internal gear. The secondary drive device can be drivingly connected to the second internal gear via a speed stage or directly. This configuration provides the advantage that the second continuously variable power distribution operating range can be realized.

前記シングル遊星歯車組は、減速歯車装置を形成し、好ましくはマイナス歯車組として構成される。マイナス歯車組とは、固定軸周りに、前記二つの異なる軸が、異なる回転方向に回転する遊星歯車である。   The single planetary gear set forms a reduction gear device and is preferably configured as a negative gear set. The minus gear set is a planetary gear in which the two different shafts rotate in different rotation directions around a fixed shaft.

この点に関して、前記ラビニヨ型遊星歯車組の少なくとも一つのエレメント、好ましくは前記遊星キャリア軸、は、特に第一クラッチ装置を介して、前記一次駆動装置（例えば内燃機関）に駆動接続することができる。前記ラビニヨ型遊星歯車組の前記同じエレメントを、電気機械によって形成されている原動機に、交互に、好ましくは恒久的に、駆動接続することもできる。   In this regard, at least one element of the Ravigneaux planetary gear set, preferably the planet carrier shaft, can be drivingly connected to the primary drive device (for example an internal combustion engine), in particular via a first clutch device. . The same elements of the Ravigneaux planetary gear set can also be drive-connected alternately, preferably permanently, to a prime mover formed by an electric machine.

前記ラビニヨ型遊星歯車組及び／又は前記シングル遊星歯車組を、前記一次又は二次駆動装置のロータの内部に配設すると、極めてコンパクトな構成を達成することができる。   When the Ravigneaux type planetary gear set and / or the single planetary gear set is arranged inside the rotor of the primary or secondary drive device, a very compact configuration can be achieved.

一方で、無段動力分配作動範囲を、他方で、それぞれ三つの歯車段を、駆動装置及び純粋に電気式の駆動装置の組み合わせのために、可能にするために、前記トランスミッションは、前記ラビニヨ型遊星歯車組の太陽歯車軸及び三つのクラッチ装置を回転停止するために、単一の制動装置のみを必要とする。
第一クラッチ装置は、前記一次駆動軸及びトランスミッション駆動軸の間に構成されている。本発明の好適な実施形態によれば、第二のクラッチ装置を前記ラビニヨ型遊星歯車組の二つの太陽歯車軸の間に配設し、第三のクラッチ装置を前記トランスミッション駆動軸及び前記ラビニヨ型遊星歯車組の前記遊星キャリア軸の間に配設することができる。 In order to allow, on the one hand, a continuously variable power distribution operating range and, on the other hand, three gear stages, for the combination of a drive and a purely electric drive, the transmission is of the Ravigneaux type Only a single braking device is required to stop the planetary gear set sun gear shaft and the three clutch devices.
The first clutch device is configured between the primary drive shaft and the transmission drive shaft. According to a preferred embodiment of the present invention, the second clutch device is disposed between the two sun gear shafts of the Ravigneaux planetary gear set, and the third clutch device is provided with the transmission drive shaft and the Ravigneaux type. It can be arranged between the planet carrier shafts of a planetary gear set.

本発明の第一実施形態において、前記無段動力分配作動範囲において、前記第一クラッチ装置のみが作動される、即ち閉じられ、これに対して、その他のクラッチ装置及び前記制動装置は作動停止される、即ち開かれる。本発明の別の実施形態において、前記第一クラッチ装置及び前記第二又は第三クラッチ装置は、少なくとも一つの無段動力分配作動範囲において作動される。前記二次駆動装置は、第二内歯車を介して前記ラビニヨ型遊星歯車組に作用する一実施形態において、前記第一及び第二クラッチ装置は第一無段動力分配作動範囲において作動され、前記第一クラッチ装置及び第三クラッチ装置は第二無段動力分配作動範囲において作動される。   In the first embodiment of the present invention, in the continuously variable power distribution operation range, only the first clutch device is operated, that is, closed, while the other clutch devices and the braking device are deactivated. That is, it is opened. In another embodiment of the present invention, the first clutch device and the second or third clutch device are operated in at least one continuously variable power distribution operating range. In an embodiment in which the secondary drive device acts on the Ravigneaux planetary gear set via a second internal gear, the first and second clutch devices are operated in a first continuously variable power distribution operating range, The first clutch device and the third clutch device are operated in the second continuously variable power distribution operating range.

前記無段動力分配作動範囲において、前記一次駆動装置は静的に作動され、前記二次駆動装置は発電機又は電動機として作動される。無段動力分配加速の場合、その加速中に、特定の限界速度まで、電流を発生することができる。更に、無段電動加速も可能である。別体の加速エレメント、例えば流体動圧トルクコンバータ、を省略することができる。前記第一クラッチ装置は、分離／接続機能のみを有し、加速クラッチとしては用いられない。   In the continuously variable power distribution operation range, the primary drive device is operated statically, and the secondary drive device is operated as a generator or an electric motor. In the case of continuously variable power distribution acceleration, current can be generated up to a specific limit speed during the acceleration. Furthermore, stepless electric acceleration is also possible. A separate acceleration element, such as a fluid dynamic pressure torque converter, can be omitted. The first clutch device has only a separation / connection function and is not used as an acceleration clutch.

少なくとも一つの歯車段作動範囲において、前記制動装置、前記第二クラッチ装置又は第三クラッチ装置が作動される。   The braking device, the second clutch device or the third clutch device is operated in at least one gear stage operating range.

本発明の、別の特に有利な実施形態において、前記第二クラッチ装置は、前記ラビニヨ型遊星歯車組の前記二つの太陽歯車軸間ではなく、前記ラビニヨ型遊星歯車組の第一太陽歯車軸と、前記シングル遊星歯車組のサマリー軸、特に前記遊星キャリア、との間に配設される。前記サマリー軸は、前記ラビニヨ型遊星歯車組の第一太陽歯車軸と前記シングル遊星歯車組の前記遊星キャリアとの間の前記駆動接続を分離することによってトルクフリーにすることができる。前記第一及び第三クラッチ装置は、上に既に記載した実施形態と同様に、同等に配置することができる。前記第二クラッチ装置、第三クラッチ装置及び制動装置から成るグループの二つエレメントが、前記第一クラッチ装置とは別に、各歯車段範囲において作動され、前記第三エレメントは作動停止される。これによって、個々の歯車段範囲において、比較的大きなスプレッドを可能にする。そして、トランスミッションの効率が更に改善される。   In another particularly advantageous embodiment of the invention, the second clutch device is not between the two sun gear shafts of the Ravigneaux planetary gear set but with the first sun gear shaft of the Ravigneaux planetary gear set. , Arranged between the summary axis of the single planetary gear set, in particular the planet carrier. The summary shaft can be torque free by separating the drive connection between the first sun gear shaft of the Ravigneaux planetary gear set and the planet carrier of the single planetary gear set. The first and third clutch devices can be arranged equally as in the embodiment already described above. Two elements of the group consisting of the second clutch device, the third clutch device and the braking device are operated in each gear range separately from the first clutch device, and the third element is deactivated. This allows a relatively large spread in the individual gear range. The transmission efficiency is further improved.

無段動力分配作動範囲から三つの歯車段作動範囲（歯車）への切り替えは、駆動作動中に行うことができる。これら三つの切り替え可能な歯車の一つでの作動中に、前記二次駆動装置は発電機又は電動機として選択的に作動され、「ブースト」（前記一次駆動装置の駆動トルクのアシスト）、「回生」、「負荷点のシフト」又は「セーリング」等のハイブリッド機能を実行することができる。電動トルクの利用はすべての歯車において行うことができる。パワーテイクオフ及び電気機械との間で少しの損失（負荷損失無し）だけ生じるため、回生中において非常に高い効率を達成することができる。   Switching from the continuously variable power distribution operation range to the three gear stage operation ranges (gears) can be performed during the drive operation. During operation with one of these three switchable gears, the secondary drive is selectively actuated as a generator or an electric motor, and “boost” (assisting drive torque of the primary drive), “regeneration” ”,“ Load point shift ”or“ sailing ”can be performed. Electric torque can be used in all gears. Since only a small loss (no load loss) occurs between the power take-off and the electric machine, very high efficiency can be achieved during regeneration.

公知のルペルシェ型トランスミッションと比較して、前記クラッチ及び制動装置が大幅に少ない。   Compared to known Ruperche type transmissions, the clutches and braking devices are significantly less.

以下、本発明を、具体的に図面を参照してより詳細に説明する。   Hereinafter, the present invention will be described in detail with reference to the drawings.

図１は、本発明による第一実施形態のトランスミッションを示す図。FIG. 1 is a diagram showing a transmission according to a first embodiment of the present invention. 図２は、前記トランスミッションの速度ラダー図を示す図。FIG. 2 is a diagram showing a speed ladder diagram of the transmission. 図３は、前記トランスミッションのスイッチングマトリクスを示す図。FIG. 3 is a diagram showing a switching matrix of the transmission. 図４は、本発明による第二実施形態のトランスミッションを示す図。FIG. 4 is a diagram showing a transmission according to a second embodiment of the present invention. 図５は、前記トランスミッションの速度ラダー図を示す図。FIG. 5 is a diagram illustrating a speed ladder diagram of the transmission. 図６は、前記トランスミッションのスイッチングマトリクスを示す図。FIG. 6 is a diagram showing a switching matrix of the transmission. 図７は、本発明による第三実施形態のトランスミッションを示す図。FIG. 7 is a diagram showing a transmission according to a third embodiment of the present invention. 図８は、本発明による第四実施形態のトランスミッションを示す図。FIG. 8 is a diagram showing a transmission according to a fourth embodiment of the present invention. 図９は、前記トランスミッションの速度ラダー図を示す図。FIG. 9 is a diagram showing a speed ladder diagram of the transmission. 図１０は、前記トランスミッションのスイッチングマトリクスを示す図。FIG. 10 is a diagram showing a switching matrix of the transmission. 図１１は、本発明による第五実施形態のトランスミッションを示す図。FIG. 11 is a diagram showing a transmission according to a fifth embodiment of the present invention.

これら実施形態において、機能的に同じ部品には同じ参照番号が与えられている。   In these embodiments, functionally identical parts are given the same reference numbers.

トランスミッション１は、すべての実施形態において、それぞれ上流側シングル遊星歯車組３を備えるラビニヨ型遊星歯車組２を備え、前記シングル遊星歯車組３は、マイナス歯車組によって形成されている減速遊星歯車組として構成されている。   In all the embodiments, the transmission 1 includes a Ravigneaux type planetary gear set 2 including an upstream single planetary gear set 3, and the single planetary gear set 3 is a reduction planetary gear set formed by a minus gear set. It is configured.

実質的にダブル遊星歯車組によって形成されているラビニヨ型遊星歯車組２は、そのそれぞれが第一及び第二太陽歯車軸１０，１３に接続された第一及び第二太陽歯車１０ａ，１３ａ並びに内歯車軸１２に接続された少なくとも一つの第一内歯車１２ａとを有する。   The Ravigneaux type planetary gear set 2 which is substantially formed by a double planetary gear set includes first and second sun gears 10a, 13a connected to the first and second sun gear shafts 10, 13, respectively, and an inner And at least one first internal gear 12 a connected to the gear shaft 12.

第一遊星歯車組１８ａが、第一内歯車１２ａ及び第二太陽歯車１３ａと噛合している。第二遊星歯車組１８ｂが、第一太陽歯車１０ａと噛合し、第一遊星歯車組１８ａと係合している。   The first planetary gear set 18a meshes with the first internal gear 12a and the second sun gear 13a. The second planetary gear set 18b meshes with the first sun gear 10a and engages with the first planetary gear set 18a.

図８及び図１１の実施形態において、ラビニヨ型遊星歯車組２は、遊星歯車１８ｂと噛合する第二内歯車２２ａを備える。   8 and 11, the Ravigneaux type planetary gear set 2 includes a second internal gear 22a that meshes with the planetary gear 18b.

前記シングル遊星歯車組３は、すべての実施形態において、太陽歯車５ａの第一ディファレンシャル軸５を備え、前記第一ディファレンシャル軸はトランスミッション１のハウジング４に恒久的に接続されている。シングル遊星歯車組２の内歯車６ａの第二ディファレンシャル軸６は、トランスミッション駆動軸７に回転可能に恒久的に接続されている。シングル遊星歯車組３の遊星キャリア８ａのサマリー軸８は、第一トランスミッション軸９を介して前記ラビニヨ型遊星歯車組２の第一太陽歯車軸１０に接続されている。パワーテイクオフは、ラビニヨ型遊星歯車組２の内歯車軸１２に恒久的に回転可能に接続されたトランスミッション出力軸１１を介して行われる。ラビニヨ型遊星歯車組２の第二太陽歯車軸１３は、第二トランスミッション軸１４と回転可能に接続されている。第一及び第二トランスミッション軸９，１４並びにトランスミッション駆動及び出力軸７，１１は、同軸に形成された中心軸として構成することができる。   In all the embodiments, the single planetary gear set 3 includes a first differential shaft 5 of a sun gear 5 a, and the first differential shaft is permanently connected to the housing 4 of the transmission 1. The second differential shaft 6 of the internal gear 6 a of the single planetary gear set 2 is permanently connected to the transmission drive shaft 7 so as to be rotatable. The summary shaft 8 of the planet carrier 8 a of the single planetary gear set 3 is connected to the first sun gear shaft 10 of the Ravigneaux type planetary gear set 2 via the first transmission shaft 9. The power take-off is performed via a transmission output shaft 11 that is permanently connected to the internal gear shaft 12 of the Ravigneaux planetary gear set 2. The second sun gear shaft 13 of the Ravigneaux type planetary gear set 2 is rotatably connected to the second transmission shaft 14. The first and second transmission shafts 9 and 14 and the transmission drive and output shafts 7 and 11 can be configured as a central shaft formed coaxially.

トランスミッション駆動軸７は、第一クラッチ装置１５及び一次駆動軸１６を介して図示しない前記一次駆動装置に駆動接続することができる。前記一次駆動装置は、例えば、内燃機関とすることができる。   The transmission drive shaft 7 can be drivingly connected to the primary drive device (not shown) via the first clutch device 15 and the primary drive shaft 16. The primary drive device can be, for example, an internal combustion engine.

図１に示した第一実施形態において、第一と第二トランスミッション軸９，１４の間に第二クラッチ装置１７が設けられ、これはラビニヨ型遊星歯車組２の二つの太陽歯車軸１０，１３の接続を可能にする。   In the first embodiment shown in FIG. 1, a second clutch device 17 is provided between the first and second transmission shafts 9, 14, which is the two sun gear shafts 10, 13 of the Ravigneaux type planetary gear set 2. Enables connection.

これに対して、図４に示した第二実施形態においては、第二クラッチ装置１７ａは、第一トランスミッション軸９とシングル遊星歯車組３の遊星キャリア８ａのサマリー軸８との間に配設され、これを介して、シングル遊星歯車組３の遊星キャリア８ａとラビニヨ型遊星歯車組２の第一太陽歯車１０ａとの間の回転接続を遮断することができる。シングル遊星歯車組３のサマリー軸８（遊星キャリア軸）は、このように、第二クラッチ装置１７ａによってトルクフリーに切り替えることができる。   On the other hand, in the second embodiment shown in FIG. 4, the second clutch device 17 a is disposed between the first transmission shaft 9 and the summary shaft 8 of the planet carrier 8 a of the single planetary gear set 3. Through this, the rotational connection between the planet carrier 8a of the single planetary gear set 3 and the first sun gear 10a of the Ravigneaux type planetary gear set 2 can be cut off. Thus, the summary shaft 8 (planet carrier shaft) of the single planetary gear set 3 can be switched to torque-free by the second clutch device 17a.

ラビニヨ型遊星歯車組２の遊星キャリア軸１８は、三つのすべての実施形態において、第三クラッチ装置１９を介して、トランスミッション駆動軸７に回転可能に接続することができる。更に、ラビニヨ型遊星歯車組２の第二太陽歯車軸１３又は第二トランスミッション軸１４は、制動装置２０によって回転停止することができる。   The planet carrier shaft 18 of the Ravigneaux planetary gear set 2 can be rotatably connected to the transmission drive shaft 7 via the third clutch device 19 in all three embodiments. Further, the second sun gear shaft 13 or the second transmission shaft 14 of the Ravigneaux type planetary gear set 2 can be stopped by the braking device 20.

電気機械によって形成されている二次駆動装置２１のロータは、ラビニヨ型遊星歯車組２の遊星キャリア軸１８に恒久的に駆動接続されている。   The rotor of the secondary drive device 21 formed by an electric machine is permanently connected to the planet carrier shaft 18 of the Ravigneaux type planetary gear set 2.

図２は、前記一次駆動装置の駆動速度をｎ１とした速度ｎのラダー図を用いて、図１に示したトランスミッション１の可能な作動モードを示している。   FIG. 2 shows possible operation modes of the transmission 1 shown in FIG. 1 using a ladder diagram of a speed n where the driving speed of the primary drive device is n1.

第二若しくは第三クラッチ装置１７，１９又は制動装置２０を作動させることによって、三つの前進歯車ｇ１，ｇ２，ｇ３を切り替えることができる。第一クラッチ装置１５は、前記一次駆動装置を切り離すために使用され、同駆動装置が二次駆動装置２１によって完全に取って代わられる時又は駆動が無い時にのみ作動停止される。   By operating the second or third clutch device 17, 19 or the braking device 20, the three forward gears g1, g2, g3 can be switched. The first clutch device 15 is used to disconnect the primary drive device and is deactivated only when the drive device is completely replaced by the secondary drive device 21 or when there is no drive.

クラッチ又は制動装置１７，１９，２０のいずれもが作動されない場合、前記ドライブトレインは無段動力分配作動範囲において作動することができ、有利には、前記一次駆動装置は静的に作動され、それに対して二次駆動装置２１は第一作動範囲ｂ１においては発電機として作動され、第二作動範囲ｂ２においては電動機として作動される。これにより、無段電動加速が可能となり、その結果、別体の加速用エレメント、例えば流体動圧トルクコンバータ又は加速クラッチを省略することができる。無段動力分配作動範囲から三つの切り替え可能な歯車ｇ１，ｇ２，ｇ３の一つへの切り替えは、駆動中に行うことができる。これら三つの切り替え可能な歯車ｇ１，ｇ２，ｇ３の一つでの作動中において、二次駆動装置２１は、例えば「ブースト」、「回生」、「負荷点のシフト」又は「セーリング」のハイブリッド機能を実行するべく、発電機又は電動機として選択的に作動させることができる。   If none of the clutches or brakes 17, 19, 20 are activated, the drive train can operate in the continuously variable power distribution operating range, advantageously the primary drive is operated statically, On the other hand, the secondary drive device 21 is operated as a generator in the first operating range b1, and is operated as an electric motor in the second operating range b2. Thereby, continuously variable electric acceleration is possible, and as a result, a separate acceleration element such as a fluid dynamic pressure torque converter or an acceleration clutch can be omitted. Switching from the continuously variable power distribution operating range to one of the three switchable gears g1, g2, g3 can be performed during driving. During operation with one of these three switchable gears g1, g2, g3, the secondary drive 21 has a hybrid function, for example “boost”, “regeneration”, “load point shift” or “sailing”. Can be selectively operated as a generator or motor.

図３は、図２に示された作動モードのためのクラッチ装置１５，１７，１９及び制動装置２４のスイッチングマトリクスを示し、”Ｘ”は各クラッチ装置１５，１７，１９又は制動装置２０の作動状態を示している。この点に関して、駆動装置２１による純粋な駆動の作動モード（歯車段範囲）ｅ１，ｅ２及びｅ３は、第一クラッチ装置１５の位置とは別に、組み合わせ駆動の作動モード（歯車段範囲）ｇ１，ｇ２及びｇ３と均等であり、これらは前進歯車並びに後進歯車とすることができる。   3 shows a switching matrix of the clutch devices 15, 17, 19 and the braking device 24 for the operation mode shown in FIG. 2, and “X” indicates the operation of each clutch device 15, 17, 19 or the braking device 20. Indicates the state. In this regard, the pure drive operation modes (gear range) e1, e2 and e3 by the drive device 21 are combined drive operation modes (gear range) g1, g2 separately from the position of the first clutch device 15. And g3, which can be forward and reverse gears.

図５は、前記一次駆動装置の駆動速度をｎ１とした速度ｎのラダー図を用いて、図４に示したトランスミッション１の可能な作動モードを示している。   FIG. 5 shows possible operation modes of the transmission 1 shown in FIG. 4 using a ladder diagram of a speed n where the driving speed of the primary drive device is n1.

第二クラッチ装置１７ａ及び制動装置２０、第二及び第三クラッチ装置１７ａ，１９、又は前記第三クラッチ装置１９及び制動装置２０を作動させることによって、三つの前進歯車ｇ１，ｇ２，ｇ３を切り替えることができる。第一クラッチ装置１５は、前記一次駆動装置を切り離すために使用され、同駆動装置が二次駆動装置２１によって完全に取って代わられる時又は駆動が無い時にのみ作動停止される。   By switching the second clutch device 17a and the brake device 20, the second and third clutch devices 17a and 19 or the third clutch device 19 and the brake device 20, the three forward gears g1, g2, and g3 are switched. Can do. The first clutch device 15 is used to disconnect the primary drive device and is deactivated only when the drive device is completely replaced by the secondary drive device 21 or when there is no drive.

クラッチ又は制動装置１７ａ，１９，２０のいずれもが作動されない場合、前記ドライブトレインは、第二実施形態においても、無段動力分配作動範囲において作動することができ、有利には、前記一次駆動装置は静的に作動され、それに対して二次駆動装置２１は第一作動範囲ｂ１においては発電機として作動され、第二作動範囲ｂ２においては電動機として作動される。これにより、無段電動加速が可能となり、その結果、別体の加速用エレメント、例えば流体動圧トルクコンバータや加速クラッチを省略することができる。無段動力分配作動範囲から三つの切り替え可能な歯車ｇ１，ｇ２，ｇ３の一つへの切り替えは、駆動中に行うことができる。二次駆動装置２１は、例えば「ブースト」、「回生」、「負荷点のシフト」又は「セーリング」のハイブリッド機能を実行するべく、三つの切り替え可能な歯車ｇ１，ｇ２，ｇ３のいずれかでの作動中に、発電機又は電動機として選択的に作動させることができる。   If none of the clutches or braking devices 17a, 19, 20 is activated, the drive train can also be operated in the continuously variable power distribution operating range in the second embodiment, and advantageously the primary drive device. Is operated statically, whereas the secondary drive 21 is operated as a generator in the first operating range b1 and as a motor in the second operating range b2. As a result, stepless electric acceleration is possible, and as a result, separate acceleration elements such as a fluid dynamic pressure torque converter and an acceleration clutch can be omitted. Switching from the continuously variable power distribution operating range to one of the three switchable gears g1, g2, g3 can be performed during driving. The secondary drive 21 is one of the three switchable gears g1, g2, g3, for example to perform a hybrid function of “boost”, “regeneration”, “load point shift” or “sailing”. During operation, it can be selectively operated as a generator or motor.

図５に示した第二実施形態の速度ラダー図は、第二クラッチ１７ａをシングル遊星歯車組３の遊星キャリア８ａとラビニヨ型遊星歯車組３の第一太陽歯車１０ａとの間に配設することによって、前記第一実施形態と比較して、個々の歯車段範囲ｇ１，ｇ２，ｇ３；ｅ１，ｅ２，ｅ３においてより大きなスプレッドが可能となることを明瞭に示している。更に、これら歯車段範囲ｇ１，ｇ２，ｇ３；ｅ１，ｅ２，ｅ３において、それぞれ一つのクラッチ／制動装置１５，１７ａ，１９，２０のみをフェードアウトさせればよいので、動力シフト能力を向上させることができる。更に、図４に示した実施形態のクラッチ装置１５，１７ａ，１９及び制動装置２０の図６に示すスイッチングマトリックスから明らかなように、燃焼動力歯車段範囲ｇ１，ｇ２，ｇ３においては四つの切り替えエレメントのうちの三つが作動（閉じる）され、電気歯車段範囲ｅ１，ｅ２，ｅ３においては二つが作動（閉じる）されるので、効率の改善も達成することができる。図５に示した作動モードにおいて、クラッチ装置１５，１７ａ，１９及び制動装置２０の前記状態が記載され、ここで、”Ｘ”は各クラッチ装置１５，１７ａ，１９又は制動装置２０の作動状態を示している。駆動装置２１による純粋な駆動の作動モード（歯車段範囲）ｅ１，ｅ２及びｅ３は、第一クラッチ装置１５の位置とは別に、組み合わせ駆動の作動モード（歯車段範囲）ｇ１，ｇ２及びｇ３と均等であり、これらは前進歯車並びに後進歯車とすることができる。   In the speed ladder diagram of the second embodiment shown in FIG. 5, the second clutch 17 a is disposed between the planet carrier 8 a of the single planetary gear set 3 and the first sun gear 10 a of the Ravigneaux type planetary gear set 3. Compared with the first embodiment, it clearly shows that a larger spread is possible in the individual gear stage ranges g1, g2, g3; e1, e2, e3. Furthermore, in the gear range g1, g2, g3; e1, e2, e3, only one clutch / braking device 15, 17a, 19, 20 needs to be faded out. it can. Further, as is apparent from the switching matrix shown in FIG. 6 of the clutch devices 15, 17a, 19 and braking device 20 of the embodiment shown in FIG. 4, four switching elements are provided in the combustion power gear range g1, g2, g3. Since three of them are actuated (closed) and two are actuated (closed) in the electric gear range e1, e2, e3, an improvement in efficiency can also be achieved. In the operation mode shown in FIG. 5, the states of the clutch devices 15, 17 a, 19 and the braking device 20 are described, where “X” indicates the operating state of each clutch device 15, 17 a, 19 or the braking device 20. Show. The operation mode (gear range) e1, e2, and e3 of pure drive by the drive device 21 is equal to the operation mode (gear range) g1, g2, and g3 of the combination drive, apart from the position of the first clutch device 15. These can be forward gears as well as reverse gears.

ラビニヨ型遊星歯車組２の内部における二次駆動装置２１及び制動装置２０の位置は、例えば空間的制約や機能的必要性の改善のために、入れ替え可能である。図７に示したトランスミッション１は、制動２０が遊星キャリア軸１８に作用し、二次駆動装置２１が（第二トランスミッション軸１４を介して）太陽歯車軸１３に作用する点において、図４に示した実施形態と異なっている。   The positions of the secondary drive device 21 and the braking device 20 inside the Ravigneaux planetary gear set 2 can be interchanged, for example, to improve spatial constraints and functional needs. The transmission 1 shown in FIG. 7 is shown in FIG. 4 in that braking 20 acts on the planet carrier shaft 18 and secondary drive 21 acts on the sun gear shaft 13 (via the second transmission shaft 14). Different from the embodiment described above.

図８及び図１１に示されているように、二次駆動装置２１が、別のエレメント、例えば第二内歯車２２ａを介して、ラビニヨ型遊星歯車組２に作用することが可能に構成することも可能である。第二内歯車２２ａは、第二遊星歯車１８ｂと係合させることができる。図８は、二次駆動装置２１が、第二内歯車２２ａに直接に駆動接続されている実施形態を示している。図１１は、二次駆動装置２１が、歯車段２３及び内歯車軸２２を介して、第二内歯車２２ａに間接的に接続されている別の例を示している。   As shown in FIGS. 8 and 11, the secondary drive device 21 is configured to be able to act on the Ravigneaux type planetary gear set 2 via another element, for example, the second internal gear 22a. Is also possible. The second internal gear 22a can be engaged with the second planetary gear 18b. FIG. 8 shows an embodiment in which the secondary drive device 21 is directly connected to the second internal gear 22a. FIG. 11 shows another example in which the secondary drive device 21 is indirectly connected to the second internal gear 22 a via the gear stage 23 and the internal gear shaft 22.

これらの実施形態は、図９に示した速度ラダー図及び図１０に示したスイッチングマトリクスから分かるように、無段動力分配作動範囲ｅｖ１に加えて、無段動力分配の第二の作動範囲ｅｖ２を実現することができるという利点を有する。図９及び図１０は、図５及び図６から、主として、第一クラッチ１５及び第三クラッチ１９が作動される追加の作動範囲ｅｖ２によって異なっている。それに対して、第一作動範囲ｅｖ１においては、図５及び図６の作動範囲ｂ１／ｂ２に類似して、第一クラッチ１５及び第二クラッチ１７ａが作動される。作動範囲ｂ１／ｂ２と同様、作動範囲ｅｖ１及びｅｖ２において、例えば電気機械によって形成されている二次駆動装置２１は、電動機又は発電機として作動可能である。   In these embodiments, as can be seen from the speed ladder diagram shown in FIG. 9 and the switching matrix shown in FIG. 10, in addition to the continuously variable power distribution operating range ev1, the second operating range ev2 of continuously variable power distribution is provided. It has the advantage that it can be realized. 9 and 10 differ from FIGS. 5 and 6 mainly by the additional operating range ev2 in which the first clutch 15 and the third clutch 19 are operated. On the other hand, in the first operation range ev1, the first clutch 15 and the second clutch 17a are operated similarly to the operation range b1 / b2 of FIGS. Similar to the operating range b1 / b2, in the operating ranges ev1 and ev2, for example, the secondary drive device 21 formed by an electric machine can operate as an electric motor or a generator.

前記一次及び二次駆動装置における「一次」及び「二次」という用語は、ここでは中立的に使用されるものであって、これら駆動装置を区別するためにのみ用いられている。一次駆動装置と二次駆動装置の両方は、主として又は主に、車両用の標準又は主駆動装置として形成され、それぞれ他の駆動装置は、一時的に切り替え可能な副駆動装置として構成することができる。これら両方の駆動装置を同じように構成して、随意交互に、標準若しくは主駆動装置として、又は副駆動装置として、使用することも可能である。更に、これらの二つの駆動装置を、シフト範囲ｇ１，ｇ２，ｇ３において、共同で等価に使用することも可能である。   The terms “primary” and “secondary” in the primary and secondary drive devices are used here neutrally and are used only to distinguish these drive devices. Both the primary drive and the secondary drive are mainly or mainly formed as standard or main drive for vehicles, and each other drive can be configured as a sub-drive that can be switched temporarily. it can. It is also possible to configure both of these drive devices in the same way and use them alternately, as standard or main drive devices, or as secondary drive devices. Furthermore, these two drive devices can be used jointly and equivalently in the shift ranges g1, g2, and g3.

Claims (20)

一次駆動軸（１６）を備える一次駆動装置を有するドライブトレインを備える、特に車両用の、トランスミッション（１）であって、
二つの太陽歯車軸（１０，１３）、一つの遊星キャリア軸（１８）及び少なくとも一つの内歯車軸（１２）を有するダブル遊星歯車を有するラビニヨ型遊星歯車組（２）並びに
減速歯車装置として形成され、かつ、歯車エレメントとして太陽歯車（５ａ）、遊星キャリア（８ａ）及び内歯車（６ａ）を備え、前記歯車エレメントの第一の歯車エレメント、特に前記太陽歯車（５ａ）がハウジングに固定されるように形成された上流側シングル遊星歯車組（３）を備えるトランスミッション（１）において、
前記ラビニヨ型遊星歯車組（２）の少なくとも第一エレメントは、特に好ましくは電気機械によって形成された二次駆動装置（２１）に、好ましくは恒久的に、駆動接続されていることを特徴とするトランスミッション（１）。 A transmission (1), in particular for a vehicle, comprising a drive train having a primary drive with a primary drive shaft (16),
Ravigneaux planetary gear set (2) having a double planetary gear having two sun gear shafts (10, 13), one planet carrier shaft (18) and at least one internal gear shaft (12), and a reduction gear device And a sun gear (5a), a planet carrier (8a) and an internal gear (6a) as gear elements, and the first gear element of the gear element, in particular the sun gear (5a), is fixed to the housing. In a transmission (1) comprising an upstream single planetary gear set (3) formed as follows:
At least the first element of the Ravigneaux type planetary gear set (2) is preferably drive-connected, preferably permanently, to a secondary drive (21), preferably formed by an electric machine. Transmission (1). 前記ラビニヨ型遊星歯車組（２）の第二エレメントは、制動装置（２０）によって回転停止可能であることを特徴とする請求項１に記載のトランスミッション（１）。   Transmission (1) according to claim 1, characterized in that the rotation of the second element of the Ravigneaux planetary gear set (2) can be stopped by means of a braking device (20). 前記ラビニヨ型遊星歯車組（２）の第三エレメント、好ましくは前記ラビニヨ型遊星歯車組（２）の第一太陽歯車軸（１０）は、前記シングル遊星歯車組（３）の第二歯車エレメントに、好ましくは、前記シングル遊星歯車組（３）の前記遊星キャリア（８ａ）に、好ましくは恒久的に、駆動接続されている、又は第二クラッチ装置（１７ａ）によって駆動接続可能であることを特徴とする請求項１又は２に記載のトランスミッション（１）。   The third element of the Ravigneaux planetary gear set (2), preferably the first sun gear shaft (10) of the Ravigneaux planetary gear set (2) is connected to the second gear element of the single planetary gear set (3). Preferably, the planetary carrier (8a) of the single planetary gear set (3) is preferably permanently drive-connected or can be drive-connected by a second clutch device (17a). Transmission (1) according to claim 1 or 2. 前記第一エレメントは、前記ラビニヨ型遊星歯車組（２）の第二太陽歯車軸（１３）又は前記遊星キャリア軸（１８）によって形成され、
前記第二エレメントは、前記ラビニヨ型遊星歯車組（２）の前記遊星キャリア軸（１８）又は前記第二太陽歯車軸（１３）によって形成されていることを特徴とする請求項１から３のいずれか一項に記載のトランスミッション（１）。 The first element is formed by the second sun gear shaft (13) or the planet carrier shaft (18) of the Ravigneaux planetary gear set (2),
4. The second element according to claim 1, wherein the second element is formed by the planet carrier shaft (18) or the second sun gear shaft (13) of the Ravigneaux type planetary gear set (2). Transmission (1) according to claim 1. 前記ラビニヨ型遊星歯車組（２）の前記第一エレメントは、第二内歯車（２２ａ）によって形成されていることを特徴とする請求項１から３のいずれか一項に記載のトランスミッション（１）。   Transmission (1) according to any one of claims 1 to 3, characterized in that the first element of the Ravigneaux planetary gear set (2) is formed by a second internal gear (22a). . 前記ラビニヨ型遊星歯車組（２）の少なくとも一つのエレメント、好ましくは前記ラビニヨ型遊星歯車組（２）の前記第一エレメント、より好ましくは前記ラビニヨ型遊星歯車組（２）の前記遊星キャリア軸（１８）は、好ましくは内燃機関によって形成されている前記一次駆動装置に駆動接続可能であることを特徴とする請求項１から５のいずれか一項に記載のトランスミッション（１）。   At least one element of the Ravigneaux planetary gear set (2), preferably the first element of the Ravigneaux planetary gear set (2), more preferably the planet carrier shaft (2) of the Ravigneaux planetary gear set (2). Transmission (1) according to any one of claims 1 to 5, characterized in that 18) can be drive-connected to the primary drive, preferably formed by an internal combustion engine. 前記シングル遊星歯車組（３）は、減速歯車装置及び／又はマイナス歯車組として形成されていることを特徴とする請求項１から６のいずれか一項に記載のトランスミッション（１）。   Transmission (1) according to any one of the preceding claims, characterized in that the single planetary gear set (3) is formed as a reduction gear device and / or a negative gear set. 前記ラビニヨ型遊星歯車組（２）及び／又は前記シングル遊星歯車組（３）は、前記一次駆動装置又は二次駆動装置（２１）のロータの内部に配設されていることを特徴とする請求項１から７のいずれか一項に記載のトランスミッション（１）。   The Ravigneaux type planetary gear set (2) and / or the single planetary gear set (3) are arranged in a rotor of the primary drive device or the secondary drive device (21). Item 8. The transmission (1) according to any one of items 1 to 7. 前記一次駆動装置軸（１６）及びトランスミッション駆動軸（７）は、第一クラッチ装置（１５）によって回転可能に接続可能であることを特徴とする請求項１から８のいずれか一項に記載のトランスミッション（１）。   9. The primary drive shaft (16) and the transmission drive shaft (7) can be rotatably connected by a first clutch device (15), according to any one of the preceding claims. Transmission (1). 前記ラビニヨ型遊星歯車組（２）の前記二つの太陽歯車軸（１０，１３）は、第二クラッチ装置（１７）によって回転可能に接続可能であることを特徴とする請求項１から９のいずれか一項に記載のトランスミッション（１）。   The two sun gear shafts (10, 13) of the Ravigneaux type planetary gear set (2) can be rotatably connected by a second clutch device (17). Transmission (1) according to claim 1. 前記トランスミッション駆動軸（７）及び前記ラビニヨ型遊星歯車組（２）の前記遊星歯車軸（１８）は、第三クラッチ装置（１９）によって回転可能に接続可能であることを特徴とする請求項１から１０のいずれか一項に記載のトランスミッション（１）。   2. The transmission drive shaft (7) and the planetary gear shaft (18) of the Ravigneaux type planetary gear set (2) can be rotatably connected by a third clutch device (19). The transmission (1) according to any one of 1 to 10. 請求項９から１１のいずれか一項に記載のトランスミッション（１）の作動方法であって、
少なくとも一つの無段動力分配作動範囲（ｂ１，ｂ２）において、前記第一クラッチ装置（１５）は作動され、好ましくは前記第二クラッチ装置（１７ａ）又は第三クラッチ装置（１９）も作動され、
少なくとも一つの歯車段作動範囲（ｇ１，ｇ２，ｇ３，ｅ１，ｅ２，ｅ３）において、前記制動装置（２０）、第二クラッチ装置（１７，１７ａ）又は第三クラッチ装置（１９）から成るグループのうちの少なくとも一つの第一装置は作動され、好ましくは前記グループのうちの別の装置も作動されることを特徴とする作動方法。 A method for operating a transmission (1) according to any one of claims 9 to 11, comprising
In at least one continuously variable power distribution operating range (b1, b2), the first clutch device (15) is operated, preferably the second clutch device (17a) or the third clutch device (19) is also operated,
In at least one gear stage operating range (g1, g2, g3, e1, e2, e3), a group consisting of the braking device (20), the second clutch device (17, 17a) or the third clutch device (19). A method of operation characterized in that at least one of the first devices is activated, preferably another device of the group is also activated. 第一無段動力分配作動範囲（ｅｖ１）において、第一クラッチ装置（１５）及び第二クラッチ装置（１７ａ）は作動され、
第二無段動力分配作動範囲（ｅｖ２）において、前記第一クラッチ装置（１５）及び第三クラッチ装置（１９）は作動されることを特徴とする請求項１２に記載の作動方法。 In the first continuously variable power distribution operation range (ev1), the first clutch device (15) and the second clutch device (17a) are operated,
13. The operating method according to claim 12, wherein the first clutch device (15) and the third clutch device (19) are operated in the second continuously variable power distribution operating range (ev2). 前記無段動力分配作動範囲（ｂ１，ｂ２）において、前記一次駆動装置及び前記二次駆動装置（２１）は作動され、
その際好ましくは前記一次駆動装置は静的に作動され、
前記二次駆動装置は電動機又は発電機として作動されることを特徴とする請求項１２又は１３に記載の作動方法。 In the continuously variable power distribution operation range (b1, b2), the primary drive device and the secondary drive device (21) are operated,
Preferably, the primary drive is then actuated statically,
The operation method according to claim 12 or 13, wherein the secondary drive device is operated as an electric motor or a generator. 少なくとも一つの歯車段作動範囲（ｇ１，ｇ２，ｇ３）において、前記一次駆動装置は過渡的に作動され、
前記二次駆動装置（２１）は電動機又は発電機として作動されることを特徴とする請求項１２から１４のいずれか一項に記載の作動方法。 In at least one gear stage operating range (g1, g2, g3), the primary drive is operated transiently,
15. The operating method according to any one of claims 12 to 14, wherein the secondary drive (21) is operated as an electric motor or a generator. 少なくとも一つの歯車段作動範囲（ｇ１，ｇ２，ｇ３）において、前記一次駆動装置は作動停止され、
前記二次駆動装置（２１）は電動機又は発電機として作動されることを特徴とする請求項１２から１５のいずれか一項に記載の作動方法。 In at least one gear stage operating range (g1, g2, g3), the primary drive is deactivated;
16. The operating method according to any one of claims 12 to 15, wherein the secondary drive device (21) is operated as an electric motor or a generator. 第一歯車段作動範囲（ｇ１；ｅ１）において、前記制動装置（２０）は作動され、好ましくは前記第二クラッチ装置（１７ａ）も作動されることを特徴とする請求項１２から１６のいずれか一項に記載の作動方法。   17. The first gear stage operating range (g1; e1), wherein the braking device (20) is operated, preferably the second clutch device (17a) is also operated. The operation method according to one item. 第二歯車段作動範囲（ｇ２；ｅ２）において、前記第三クラッチ装置（１９）は作動され、好ましくは前記第二クラッチ装置（１７ａ）も作動されることを特徴とする請求項１２から１７のいずれか一項に記載の作動方法。   18. In the second gear stage operating range (g2; e2), the third clutch device (19) is operated, preferably the second clutch device (17a) is also operated. The operation | movement method as described in any one. 第三歯車段作動範囲（ｇ３；ｅ３）において、前記第二クラッチ装置（１７ａ）は作動されることを特徴とする請求項１２から１８のいずれか一項に記載の作動方法。   The operating method according to any one of claims 12 to 18, wherein the second clutch device (17a) is operated in a third gear stage operating range (g3; e3). 第三歯車段作動範囲（ｇ１；ｅ１）において、前記第三クラッチ装置（１９）及び前記制動装置（２０）は作動されることを特徴とする請求項１２から１８のいずれか一項に記載の作動方法。   The third clutch device (19) and the braking device (20) are operated in a third gear stage operating range (g1; e1), according to any one of claims 12 to 18. Actuation method.
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